Brake for pressfeeder

ABSTRACT

There is disclosed herein brake instrumentalities and means for controlling the same which are associated with roll-feeding mechanism to regulate roll rotation of material fed therebetween, such mechanism being shown in this instance in association with a high-speed punch press, to which the strip material fed through the feeding mechanism is supplied for operation by the punch press, the precise positioning of the material being affected by the brake instrumentalities hereof which are adapted for incremental feeding of such material. The brake mechanism involves the provision of a compact housing in which are located a pressure plate, suitable friction plates, a brake disc which in turn is connected to at least one of the rolls through which the material is fed, all under the control of an hydraulic piston and cylinder arrangement which provides the power to actuate the brake mechanism under the control of certain hydraulic booster elements which are actuated in response to and in timed relation to motion of the crankshaft of the press by hydraulic means provided for such booster actuation and adjustable in accordance with the desired amount of rotation of the rolls to feed the said material to the aforementioned press.

United States Patent [72] inventors Oscar E. Pax

R.R. #5 Box 400-A. Celina. Ohio 45822: Francis J. Fax, 624 Plum Drive, Coldwater, Ohio 45828 [211 App]. No. 795,482

[22] Filed 1:11.31, 1969 [45] Patented July 6, 1971 Primary Examiner-Charles W. Lanham Assistant Examiner-R. M, Rogers Anorney-Robb & Robb ABSTRACT: There is disclosed herein brake instrumentalities and means for controlling the same which are associated with roll-feeding mechanism to regulate roll rotation of material fed therebetween, such mechanism being shown in this instance in association with a high-speed punch press, to which the strip material fed through the feeding mechanism is supplied for operation by the punch press, the precise positioning [54] BRAKE FOR PRESSFEEDER 5 Claims, 10 Drawing Figs of the material being affected by the brake instrumentalities hereof which are adapted for incremental feeding of such [52] U.S.Cl 72/419, materiai The brake mechanism involves the provision f 3 72/425 compact housing in which are located a pressure plate, suita- [5 l Int. Cl. 821d 43/02, ble f i i flaws, a brake disc which in mm is connected to at B65h l7/00 least one of the rolls through which the material is fed, all [50] Field of Search 72/421, under the comm] f an hydraulic piston and cylinder arrange. 1 425; 226/145, 156 ment which provides the power to actuate the brake 56 R f ed mechanism under the control of certain hydraulic booster elel 1 e It ments which are actuated in response to and in timed relation UNITED STATES PATENTS to motion of the crankshaft of the press by hydraulic means 2,168,284 8/1939 Crane 226/145 provided for such booster actuation and adjustable in ac- 2,758,837 8/1956 Littell 226/145 cordance with the desired amount of rotation of the rolls to 3,078,734 2/1963 Wiig 226/156 feed the said material to the aforementioned press.

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INVQNTORS #1 F? J- P/M BRAKE FOR PRESSFEEDER A particular object of the invention is to provide brake instrumentalities which will precisely stop the feeding of material to the press, be variable in the sense that it will be responsive to preset conditions and mechanism which determines when the brake instrumentalities should be actuated, and the brake instrumentalities are in turn actuated hydraulically with sufficient pressure to effect the desired stopping as movement of the material is intended to be arrested.

A particular object of the invention is to provide hydraulic brake instrumentalities which will be responsive to a booster for actuation, the booster in turn being periodically actuated when certain cycles of press operation are accomplished, braking action being provided by the brains instrumentalities to maintain the material position and stopping action additionally provided by said instrumentalities as heretofore out-- lined.

Another object of the invention is to provide a hydraulic booster unit which is actuated in response to periodic impulses transmitted thereto in the cycle of operation of the press, which impulses are translated to the brake instrumentalities at appropriate times to arrest the movement of material passing through the rolls controlled by the brake instrumentalities which rolls are incorporated in the feeding mechanism.

A particular object of the invention is to arrange the brake instrumentalities in a compact manner so that the same may be mounted closely adjacent the rolls, and in fact upon the shaft of one of such rolls which shaft is driven by suitable gear mechanism, the brake instrumentalities incorporating a pres sure plate of a form including piston elements thereon, the pressure plate being restrained against rotative movement in respect to the housing for the brake instrumentalities, the brake disc spaced from the pressure plate with suitable friction means interposed therebctween, application of pressure to the plate and the frictional engagement with the brake disc effecting the stopping action. The foregoing ir the result of very minute movements of the plate which are in turn the result of minute movements of the booster to impart the hydraulic pressure for the stopping action.

A particular object of the invention is to arrange the booster in such a manner that the movement of the piston and cylinder elements therein are translated by hydraulic connections to the brake instrumentalities with certain adjusting and corn pensating means provided for the pressure applied, both in the booster and at the brake instrumentalities whereby the brake instrumentalities may be operated with greater or less speed depending upon the speed of feed of the material being corre lated therewith.

Other objects of the invention will include the arrangement of the various parts including certain valves to provide initial braking force for application to the rolls to maintain the same against undesired rotation, and permit additional braking force or stopping force to be applied when necessary in accordance with the heretofore outlined provisions of the various parts mentioned.

Other and further objects of the invention will be understood from a consideration of the specification appended hereto and disclosed in the drawings wherein:

FIG. 1 is a side view of a press incorporating the feeding mechanism and showing the relationship of the booster and braking instrumentalities with a general provision for operation and adjustment disclosed.

FIG. 2 is a fragmentary view in somewhat enlarged detail of a portion of the feeding mechanism to illustrate the drive for the feed rolls.

FIG. 3 is an end view of the feeding mechanism taken op posite that end shown in FIG. 2 to disclose the position of the brake instrumentalities and housing therefor.

FIG. 4 is a fragmentary view, partly in section, showing in greater detail the brake mechanism and instrumentalities incorporated therein with certain connections.

FIG. 5 is an enlarged sectional view showing the hydraulic booster, including the operating elements thereof, and connections for operation by the press.

FIG. 6 is a sectional view through a pressure control valve used in the circuit.

FIG. 7 is a view in elevation, showing the brake disc as removed from the brake unit.

FIG. 8 is an end view of the disc shown in FIG. 7.

FIG. is a side view of the pressure plate.

FIG. 10 is an end view ofthe pressure plate shown in FIG. 9.

Referring now to FIG. ii, there is disclosed generally a highspeed press having a base ll upon which is supported the upright main frame 2, said main frame including a bed 3, the upper portion of said main frame having mounted thereon a crankshaft 4' at one end of which is located a flywheel 5, said crankshaft t having a throw indicated at 6 to which the ram 7 is pivotally connected, the ram 7 being adjustably arranged with respect to said throw 6 in the usual manner, and the ram '1 being guided for vertical reciprocating movement, as is usual in press construction.

At the end of the crankshaft 4 opposite the flywheel 5, is an adjustable eccentric member 8 which provides for a sliding connection to the end 9 of an hydraulic piston and cylinder unit 10, the piston rod being denoted 11 therein. The end of the rod it upon which the member 9 is mounted is pivotally connected and adjustable along a slot 12 in the eccentric 3 referred to, to vary the stroke of the unit 10.

The hydraulic piston and cylinder unit 10 is in turn connected to a further hydraulic piston and cylinder unit 13 by the hoses M and 15, said hydraulic piston and cylinder unit 13 being arranged in a vertical manner with the piston rod 16 thereof having a gear rack 17 at its lower extremity.

The feeding mechanism with which the invention hereof is associated, is shown as being supported at one side of the bed 3 including a main support 18, which includes a base frame W, from which base frame l9 extends upwardly a pair of upright frame members 20 and 21. As indicated in FIGS. 2 and 3, the franc members 20 and 21 support a pair of rolls 22 and 23 for rotation, in suitable bearings supplied, and by a drive gear I2 1 connected to the shaft 25 of the roll 23, so that rotation of said gear 24 will impart corresponding rotation to the shaft 225 and the roll 23 carried thereby.

At the opposite end of the shaft 25 is a further gear 26 indicated in FIG. 4, which is engaged with a gear 27 on the shaft 28 ofthe upper roll 22.

with this arrangement rotation of the gear 24 will impart simultaneous rotation to the rolls 23 and 22, but in the opposite directions. It should be noted that the drive from the gear 24 to the shaft 25 is effected through a one-way clutch 30 of conventional form not shown in detail, so that when the gear M is rotated in one direction, drive will be imparted thereto by the rack 1'7 in its downwardly reciprocating action, for example, but in view of the one-way clutch 30 upward movement of the rack i7 will merely return the gear 24 to an initial position for subsequent drive when the rack 17 is moved downwardly again.

All of the foregoing structure is described in detail and the operation of the feeding mechanism outlined completely in copending application Ser. No. 687,687 filed Dec. 4, 1967, together with certain control means therein which are not described in detail herein but are required for the complete operation of the press hereof in its feeding action as imparted to the feeding mechanism which has been generally described and in some detail set forth. Suffice it to say, the invention hereof is incorporated largely in the brake mechanism and its associated controls, whereby improved feed-roll control and actuation is effected over that disclosed in the prior application heretofore mentioned in which prior application a simple friction brake was availed of.

The important advance in this particular application resides in the fact that the brake assembly hereof does not develop the heat and therefore the loss of efficiency which is present in high-speed presses where the roll movement is necessarily extremely rapid and stopping action required to be much more critical by reason of the inertia forces present.

In any event, this invention is shown in detail in the other figures herein, involving particularly FIG. 4 where is disclosed the brake mechanism specifically and instrumentalities incorporated therein, involving a housing generally denoted 32 which is generally circular as to the body thereof, having an extension section 33 at one end, and at the other a cover plate 34 which extends below the housing 32 and incorporates therein means to stabilize the housing and indicated at 35 in the form of an inverted U-shaped section engaging a post which extends from the base frame 19 previously mentioned.

Within the housing 32, there is mounted a bralce disc 36 more particularly shown in FIGS. 7 and 8, as comprising the disc portion 37 of relatively large diameter and integrally formed with a hub 3ft, which hub is in turn formed with a gearengaging section 39, the latter having the keyway Ml therein, whereby the said disc 36 is keyed to the gear 26, a further keyway 41 within the extension 39 being provided to key the disc to the shaft 25.

It will therefore be apparent that the rotation of the shaft 25 will impart rotation to the disc 36 and through the disc and specifically the section 39 thereof, to the gear 2e and thereby to the upper gear 27 as previously suggested.

In any event, the disc 36 provides for support of the housing 32 thereon by means of a suitable ball bearing race 42, said race being mounted in the cover 34 as noted in FIG. 4.

Within the hub 38 of the disc 36, additional ball bearing races 43 and 44 are shown, to provide for the support of a pressure plate, generally indicated at 45 and more particularly shown in detail in FIGS. 9 and 10.

The pressure plate 45 includes a piston section 436 formed integrally with a relatively large diameter plate portion 47 and having a suitable O-ring groove 48 formed in said piston section 46. v

Extending from the opposite side of the piston section 416 is a cylindrical member 49 being integral with th" ate section 47 and section 46 to provide for support by d and 44 previously mentioned.

The extension 49 is equipped as shown i1 suitable washer member 50 maintained not. ti end of the extension 49 by a suitable capscrew iii to provide for positioning of the pressure plate $5.

The housing 32 is formed with an inwardiy extending sec tion 52 having a pressure surface arranged in alignment with the outer circumferential area of the disc 36, and specifically the portion 37 thereof, which together with the provision of certain friction elements in the form of washerlilae disc parts 53 and 54 upon application of suitable pressure to the pressure plate 45 compel slowing or stopping rotation of the brake disc 36 and specifically against the section 37 thereof.

In order to effect this action of course, the pressure plate 45 is provided with suitable notches 55 at its periphery which notches engage dowel pins 56a extending through the outer section of the housing 32. permitting reciprocation of the pressure plate 45 but preventing relative rotation between such plate and the housing.

In order to provide for movement of the pressure plate, the piston section 46 thereof is mounted in the extension 33 acting as a cylinder portion, of a first hydraulic piston and cylinder set.

In order to effect actuation of this pressure plate in reciprocating movement, the passage 56 is provided leading to a regulator unit 57 in the form of a flow control valve as shown in FIG. 6, by a pressure fluid supply passage 58. The passage 58 is connected to a passage 59 as indicated in FIG. 6 leading to the pressure chamber 60 in the unit 57. The unit 57 is shown in section and detail in FIG. 6 as comprising a body section 63 having an offstanding portion 64 in which is mounted needle member 65 maintained in close to a seated position by an adjusting screw 67 to permit a small amount of oil to flow to the low pressure side during braking.

The passage 59 is connected to the lower end of the body section 63 to the chamber 60 near a check member 68 positioned by a spring 69 against a seat 70, there being a bypass or fluid passage '71 extending from a position below the check member 68 to the seat area 72 controlled by the needle member 65 whereby to permit a certain amount of hydraulic fluid to pass from one side to the other without affecting the check member 68.

The upper end of the section 63 of this valve 57 now being described, is connected by line 73 to a source of air pressure which is preferably adjusted to about 20 pounds per square inch, which pressure is exerted against a column of oil in the line 73 so that this pressure is in turn of course exerted against the check member 63.

This pressure may be regulated by a suitable regulator indicated at '74.

An hydraulic booster which is in the circuit that is presently being described is shown in detail in FIG. 5, and includes a body 75 in which two piston and cylinder sets are arranged, one piston and cylinder set being indicated as including the piston 76, a suitable O-ring seal 77 disposed thereon, movable in the cylinder 7% to exert hydraulic pressure on a chamber 79.

The piston rod fill of this piston and cylinder set extends upwardly through a cover fill and is engaged by a sleeve 82 which sleeve 82 is maintained in position on the piston rod by a setscrew $3, and in turn is adapted to receive a rod 84.

The rod 8 as indicated in FIG. I is disposed beneath the lower end of the raclt l7 and adapted to be impinged thereby so as to impart downward pressurizing action to the piston 76 in the manner and for the purposes to be hereinafter set forth.

The chamber 79 is covered by a bottom plate 84a in which a passage 85 is formed leading to a passage 86 which is in turn connected by a pipe 87 extending to the passage 58 previously mentioned.

Also formed within the housing 75 is a second piston and cylinder set, involving a piston 89 having a suitable O-ring seal 9% thereon, said piston being adjustably positioned within a cylinder 91 and engaged by a spring 92, which spring 92 is adapted to be adjusted as to tension by a suitable setscrew 93 iocket in position by a locknut 94.

It is apparent that the movement of the piston 76 downwardly, if no other forces are present, will normally transmit the fluid pressure developed in the chamber 79 through the passage 86, in turn through the pipe 87 to the brake instrumentalities previously described in detail and shown in FIG. 4;, to immediately act on check member 68 to close the same more tightly, but if undue pressure is developed, such pressure will be relieved by the operation of the piston 89 in LIKE cylinder 9 of the housing 75.

Since the fluid pressure normally existing within the system is preset at 26 pounds by the provision of the valve 74, for equalization of fluid on both sides of the check member 68, there will normally be exerted on the brake instrumentalities a 20-pound per square inch pressure, which by reason of the frictional engagement of the respective discs, friction members and pressure plate restrains the rolls 22 and 23 from rotation. This is necessary because of the various forces present in moving material between the rolls and the desirability of holding the material and maintaining the same in a relatively firmly guided position. The frictional engagement is such that the material can be moved by the rack 17 against the braking force developed in the braking instrumentalities, and when the raclt 17 reaches the bottom extent of its movement and impinges against the rod 84, a rapid development of the hydraulic pressure in the cylinder and piston unit and specifically in the chamber 79 will be imparted to the brake instrumentalities. This will momentarily increase the braking pressure and cause a stopping force to be exerted therewithin and stop the rotation of the rolls thereby.

Reiterating certain specific aspects of the operation of the mechanism heretofore described, it is noted that the air regulator 74 which is an air regulator, and directs air pressure to the column of oil indicated in FI G. 4 as standing in the line 73 above the valve 57, is set for about pounds per square inch. Such air pressure, through the oil supply contained in the air line as stated, applies a preloading pressure in the brake system to provide a small amount of drag so to speak, on the feed rolls 22 and 23, to prevent any reversing action which might be caused by a loop in the material for example.

The check member 68 of this valve is so arranged as to permit thispreloading pressure to equalize throughout the entire system with only a small pressure loss.

When the rack 17 approaches the end of its feed stroke, it will come in contact with the rod 84. This contact for example, may take place at a position about one sixteenth of an inch from the bottom of the full stroke of the rack 17. When the rack 17 makes this contact with the rod 84, it also transmits such contact to the piston rod 80 and the piston 76 connected thereto. Such contact immediately increases the pres sure through the system. This increased pressure causes a sealing positioning of the member 68 in the valve 57 and prevents higher pressure oil from returning to the oil supply line. This increasing pressure will intensify the braking pressure through the piston section 46 connected to the plate section 47, reference being had to FIG. 4. When the pressure thus developed is enough to overcome the action of the spring 92 in the hydraulic booster shown in FIG. 5, the piston 89 is moved upwardly as shown in that FIG. 5, to make room for the oil displaced by the continued movement of the piston 76. The piston 76 continues to move until it comes in contact with the bottom plate 84a. At this point in the operation, the movement of the rack 17 will stop as will all feeding movement. During this increased pressure portion of the feeding cycle, a small amount of oil has been allowed to return to the oil supply line 73 around the needle member 65 of the valve shown in FIG. 6, the oil pressure being maintained through spring pressure on the piston 89. When the rack 17 reverses and moves upwardly, the piston 76 will likewise move upwardly toward the cover 81, the piston 89 returning to its position adjacent the plate 840. At this time also, the check member 68 will be unseated to permit replacing the oil displaced through the needle member 65, and the system thus return to the preloaded pressure condition.

It has been found necessary to permit a small amount of oil flow around the needle member 65 as explained, and to thereafter be replenished.

One of the advantages of the relatively low preloading pressure of 20 pounds per square inch which has been mentioned herein, is to permit a pilot which may be positioned in the die in the press with which this mechanism is associated, to facilitate positioning of the material by pulling the material a small amount with relatively small effort, even though the rolls must be rotated slightly to do this.

It will be seen from this that substantial variations in pressure may be developed for both braking and stopping forces, and since the motion, that is the extent of motion of the rack 17 may be adjusted, positions at which actuation of such mechanism as has been herein described, may be varied within relatively wide limits.

In order to effect a variation of the amount of material fed through the mechanism within very narrow limits, the rod 84 may be removed and a shorter or longer rod substituted therefor, this being etfected by having rods of closely calculated lengths available for such purpose.

We claim:

1. in combination with a press of the class described, feeding mechanism comprising a base frame mounted on the press, spaced upright frame members on said base frame, a pair of rolls carried by said members to engage upper and lower surfaces of material inserted therebetween, means to rotate said rolls to move such material into the press in uniform step-bystep increments for forming, comprising a reciprocable member, brake instrumentalities in said mechanism including means to exert a predetermined braking force on the rolls to prevent rotation thereof which would result in nonuniform material movement, and elements actuated by the roll-rotating means to direct stopping force to the instrumentalities and thereby the rolls, to maintain the material in position while forming is effected, said elements including an hydraulic booster actuated by said member, pressure developed by said booster being transmitted to the instrumentalities, said instrumentalities being mounted in a housing and having a brake disc connected to the rolls, friction means adjacent said disc, a pressure plate nonrotatively positioned in the housing, piston and cylinder means to move the plate toward the disc and friction means to stop disc rotation, said piston and cylinder means having the pressure aforesaid directed thereto.

2. Feeding mechanism as claimed in claim 1, wherein said booster comprises a first piston and cylinder set in which the piston is movable directly by the member, and a second piston and cylinder set to adjust the pressure delivered by the first set, pressure developed by said booster being transmitted to the instrumentalities.

3. Feeding mechanism as claimed in claim 1, wherein the rolls are rotated by gears, a rack engages at least one gear to rotate the same, said rack being hydraulically reciprocated in adjustable timed relation to the press, said rack periodically engages said hydraulic booster to effect development of the stopping force, said booster including piston and cylinder parts, pressure developed by said parts being directed to the piston and cylinder means in the brake instrumentalities, said instrumentalities including a housing, a pressure plate directly engaging said piston and cylinder means, said plate being reciprocable and rotatively restrained with respect to the housing, friction means adjacent the plate, a disc adjacent the friction means, said disc being connected to one of the rolls to direct braking force thereto, hydraulic pressure developed by the booster in excess of the braking force continuously exerted in the instrumentalities providing the force for stopping roll rotation.

4. Feeding mechanism as claimed in claim 3, wherein said booster comprises a first piston and cylinder set in which the piston is movable directly by the member, and a secton piston and cylinder set to adjust the pressure developed by the first set.

5. Feeding mechanism as claimed in claim 3, wherein means are provided to adjust the speed of operation of the piston and cylinder means. 

1. In combination with a press of the class described, feeding mechanism comprising a base frame mounted on the press, spaced upright frame members on said base frame, a pair of rolls carried by said members to engage upper and lower surfaces of material inserted therebetween, means to rotate said rolls to move such material into the press in uniform step-by-step increments for forming, comprising a reciprocable member, brake instrumentalities in said mechanism including means to exert a predetermined braking force on the rolls to prevent rotation thereof which would result in nonuniform material movement, and elements actuated by the roll-rotating means to direct stopping force to the instrumentalities and thereby the rolls, to maintain the material in position while forming is effected, said elements including an hydraulic booster actuated by said member, pressure developed by said booster being transmitted to the instrumentalities, said instrumentalities being mounted in a housing and having a brake disc connected to the rolls, friction means adjacent said disc, a pressure plate nonrotatively positioned in the housing, piston and cylinder means to move the plate toward the disc and friction means to stop disc rotation, said piston and cylinder means having the pressure aforesaid directed thereto.
 2. Feeding mechanism as claimed in claim 1, wherein said booster comprises a first piston and cylinder set in which the piston is movable directly by the member, and a second piston and cylinder set to adjust the pressure delivered by the first set, pressure developed by said booster being transmitted to the instrumentalities.
 3. Feeding mechanism as claimed in claim 1, wherein the rolls are rotated by gears, a rack engages at least one gear to rotate the same, said rack being hydraulically reciprocated in adjustable timed relation to the press, said rack periodically engages said hydraulic booster to effect development of the stopping force, said booster including piston and cylinder parts, pressure developed by said parts being directed to the piston and cylinder means in the brake instrumentalities, said instrumentalities including a housing, a pressure plate directly engaging said piston and cylinder meanS, said plate being reciprocable and rotatively restrained with respect to the housing, friction means adjacent the plate, a disc adjacent the friction means, said disc being connected to one of the rolls to direct braking force thereto, hydraulic pressure developed by the booster in excess of the braking force continuously exerted in the instrumentalities providing the force for stopping roll rotation.
 4. Feeding mechanism as claimed in claim 3, wherein said booster comprises a first piston and cylinder set in which the piston is movable directly by the member, and a secton piston and cylinder set to adjust the pressure developed by the first set.
 5. Feeding mechanism as claimed in claim 3, wherein means are provided to adjust the speed of operation of the piston and cylinder means. 